Regulating devices provided with friction-free valves



mm 1%, 194 2. R1 ALDSON 2,304,74

REGULATING DEVICES PROVIDED WITH FRICTION-FREE VALVES Filed Nov. 1, 1940 2 Sheets-Sheet l A ATTORNEY Defl 1%42. R. R. DoNAmsQM REGULATING DEVICES PROVIDED WITH FRIGTION-FRE IE VALVES Filed Nov. '1, 1940 2 sheets sheet '2 AT TORNEY BEGULATING DEVICES PROVIDED.WITB

FRICTION-FREE VALVES Robert R. Donaldson, Forest Hills, Pa. Application November 1, 1940, Serial No. 388,882

This invention relates to pressure-actuated devices oi the type embodying a pressure-sensitive mber such for example as'a diaphragm, and a control member, for example a valve, actuated by the pressure-sensitive member and more particularly to a device that shall be provided with means which for all practical purposes trees the valve or control member oi static friction. whereby the device may be rendered more sensitive to minute pressure changes acting on the pressurescnsitive member.

An object or this invention is to provide a pressure-actuated device having means for eliminating, for substantially all practical purposes, all static friction in its control member so that the pressure-actuating member tor the control member will be rendered more eflective in accurately initiating movement of and positioning the control member in response to pressure changes.

Another object of the invention is to provide a pressure-sensitive device of the type referred to above, having means for continually eflecting relative movement between the control member 'or valve and the ported member of the valve in two planes simultaneously so that the control member may be free of static iriction when moved in the direction in which it is actuated by the pressure-sensitive member.

Other objects of the invention will be apparent ,to'those skilled in the art from the following description taken in conjunction with the accompanying drawings in which:

Figure lis a view in vertical section of a device, parts thereof being broken away, embodying what now appears to be a preferred form of the invention;

Fig. 2 1s a view in vertical section 501 the upper portion of the device shown in Fig. ,1;

Fig. 3 is a top plan view of certain structural details embodied in the device shown in Fig. 1;

Fig. 4 is a view in vertical section of a valve and valve sleeve embodied in the device shown 'in Fig. 1;

Fig. 5 is a top plan view of the valve and valve sleeve shown in Fig. 4;

Fig. 6 is a view in section taken on line VI--VI of Fig. 4; and

Fig. '7 is a more or less diagrammatic view of the device shown in Fig. 1 as applied in the control of a power cylinder which may be used to actuate any regulating device such as a damper or valve.

Throughout the drawings and the specification like reference characters indicate like parts,

-In the drawings, and with particular reierenco to Fig. 1, a device I is-shown which now appears to embody a preferred iorrno! the invention. The device comprises a pressure-sensitive member 2, such as a diaphragm, disposed in a chamber or housing 3 and a control means I such as a valve, whose control element or valve member is operatively connected to the diaphragm by means 4 in such manner that movement oi the diaphragm in response to changes in the pressure acting thereon results in corresponding changes in the control position of the control element or valve member.

Valve means 6 controls the pressure at which a power medium, such as water or ofl, or other -.huid, is discharged at the outlet port or ports thereof, the valve being connected to a supply source 01' power medium whose pressure is preterably maintained substantially constant at the inlet of the valve.

In cases where the power medium is delivered by the valve to an actuating device such as a power cylinder having a reciprocating piston therein, the valve is constructed preferably with two outlet ports and two discharge ports, one outlet being connected to one end of the power cylinder and the other outlet being connected to the opposite end of the cylinder. Thus, as the valve is moved within its range of travel the pressure medium is delivered to one end or the other of the cylinder and is exhausted from the opposite end causing the piston to move in one direction or the other at verying rates of speed, depending on the pressure 01' the fluid acting on the piston. If both outlets of the valve are closed or open slightly to the same extent, the piston remains stationary because the forces acting on its opposite faces are in balance.

Movement of the piston of the power cylinder when utilizedto control the pressure of a gas or fuel, or the pressure in the combustion chamber of a furnace, ailects the positioning of a damper or valve, and this damper or valve controls the pressure or pressures to which diaphragm 2 responds. Thus if device I is utilized for regulating pressures and maintaining such pressures constant within very small limits, the diaphragm would be subjected to the pressure which is controlled by the damper or valve which in turn is actuated by the piston 01' the power cylinder, the power cylinder being under control of device I.

Valves of the type illustrated by Fig. 4 are ordinarily subject to considerable static friction. Where considerable static friction is involved, it

follows that the pressure change on the operating diaphragm or pressure-sensitive member must be considerable at times to first free the valve before it can be moved. By the time movement of thevalve has been effected, the change in pressure acting on the diaphragm and calling for a change in position of the valve will have exceeded by a considerable amount the valuepermitted for good regulation, because of the excessive change in pressure required to first overcome the static friction of the valve.

In order to obtain eflicient and quick response to pressure changes, the valve actuated by the diaphragm or pressure-sensitive member, should be free of static friction. In particular, the valve should be free of static friction in the direction in which it is moved by the pressuresensitive member, and preferably the valve should be free of friction in a direction normal to its line of motion as well.

Another factor which is equivalent of static friction or behaves in a manner similar to static is the factor of adhesion. The adhesion factor comes into play only when there is flow throughout the valve. Nearly all valves when near their neutral or closed position have a tendency to he held in that position by a force which I designate as adhesion and is caused when there is flow of liquid, fluid or gases through the valve. Therefore, a valve to be free of static friction, for all practical purposes, must also be free of the factor of adhesion when it is near its neutral or closed position.

In accordance with this tion including the adhesion factor is for all practical the valve about its longitudinal axis and continually vibrating the valve in a direction coincidental with its longitudinal axis. It is preferred to so construct the valve that nodeless vibration is obtained and so that the amplitude of vibration is the valve is in neutral or closed position and which diminishes to a lesser but effective amplitude as the valve is actuated away from its neutral or closed position.

As shownin Fig. I having a bore 6 for receiving a ported valve sleeve I, within which a valve stem 8 is disposed and provided with a plurality of lands 8, l0, II, and I2. The ports in sleeve I may he formed directly in the valve body if desired, but manufacinvention, static friceliminated turing considerations make it desirable to employ a sleeve.

The valve body is provided with an inlet II to which a supply of power medium, such as oil or water or other suitable fluid is connected. In the drawing, a pump II is shown as a means of supplying the power medium, the outlet of the pump being connected to a pipe ii to the inlet of the valve body. The valve body is formed with outlet ports 16 and I! which are connected to tapped outlet connections II and ii, to which, as is shown in Fig. 7, the opposite ends of a power cylinder 20 are connected by pipes 2| and 22, respectively. The valve body also is provided with outlet ports 23 and 24 through which oil or be exhausted from one end or the other of the power cylinder. The oil or liquid discharging from the valve may be caught in a reservoir or tank 2! in which the pump is located and is repumped by the pump to the valve inlet ii; in other words, the fluid system is of the closed type, although this is not essential except in so far as wastageoi the fluid may be a factor.

The construction of sleeve 1 and valve stem I 1, the valve comprises a body water may is shown more clearly to a larger scale in Fig. 4. l The sleeve is machined to have a fluid-tight fit with bore 6 of the valve body and its upper end is enlarged and threaded so that the sleeve may have screw thread adjustment of position relative to the inlet, outlet, and exhaust ports of the valve The sleeve is provided with annular grooves 26, 21, 28, 29, and 30, which, when positioned in the. valve body, lie in communication with the inlet, outlet, and exhaust ports of the valve body as shown in Fig. 1 and as indicated by the legends on Fig. 4. On diametrically opposite sides of the sleeve the bottom of each groove is machined flatwise or on the straight to a depth sufilcient to cut through the wall of the sleeve whereby pairs of ports 3l-3l, 32-32, 33-33, 34-34, and 35-35 are formed. These ports provide communication between the inlet port I3 and the interior of sleeve I, that is the bore of sleeve 1 in which valve stem 8 is dispose and communication between outlet ports and e haust ports and the interior of the sleeve.

Valve stem 8 is made from a rod of suitable metal such as stainless steel, for example, or other suitable alloy whose diameter is such as to provide a neat flt with the bore of sleeve 1. This valve stem is machined to provide lands 9, H), H, and H as shown in Figs. 1 and 4. Lands 9 and i2, respectively, are positioned one above and below ports 23 and 24 so as not to interfere with the discharge or exhaust of fluid from either body.

" end of power cylinder 23 but will effectively prevent leakage of fluid through either end of sleeve I. The spacing of lands ill and ii is equal to the spacing of the pairs of ports 32-32 and 34-34 and thereby controls the delivery of fluid to one end or the other of the power cylinder and the discharge from the opposite end thereof through one or the other of the exhaust ports.

As may be seen by inspectionof Figs. 1 and 4, the portions of stem 8 located between the lands a, in, H, and i2, are considerably smaller inniameter than the main body of the stem. By making these portions of reduced diameter space is provided in which the fluid may flow from the inlet port to either of the outlet ports ll anQfll or from the ends of the power cylinder 2! to the exhaust ports 23 and 24.

When valve stem I is in the position shown in Figs. 1 and 4, lands 3 and" are in neutral or closed position. 'When in this position the cohes'lon factor exerts a force tending to hold the valve stem in this position. Likewise the static friction between the valve stem and the bore of valve sleeve 1 tends to hold the valve stem against movement. To overcome both the static friction and the factor of cohesion, means 21 are provided for effecting relative rotation between the valve stem 8 to sleeve I about the longitudinal axes thereof. This would be the vertical axis of the valve and sleeve with reference to the position in which the regulating devic lis shown mounted in Fig. 1. Static friction and the factor of cohesion are further overcome by so designing the valve and the mass in the connecting means l that the waive will vibrate in a direction normal to its direction of spinning, which as shown-in the drawing is coincidental with the longitudinal axis of the valve stem. I may produce relative rotation between the ported sleeve 1 and valve element 8 by rotating either the sleeve or the stem, or both, but for manufacturing reasons in so far as the form shown in the drawings is concerned, I prefer to spin valve element I and hold sleeve 1 in a stationary position. Of course, if the ports of. sleeve 1 are formed in the valve body; in whichcase the sleeve would be omitted, valve element {would be spun and vibrated. Even though sleeve 1 were spun, I would still so design the valve that valve element 8 would vibrate.

An eflective and simple means for producing vibration oi! the valve stem may be accomplished by designing the valve with lead. The term lead" means that valve lands l and II are made slightly smaller than the openings of ports 32-32 and 34-34, respectively, so that these ports are never completely covered when the valve stem is in neutral or closed position. Thus, when this valve is in neutral position and fluid is supplied to the inlet of the valve there will be leakage past valve lands l0 and II to the exhaust ports 23 and 24. Owing to the fact that this leakage cannot be exactly proportioned there results a slight unbalance in the valve, and this slight unbalance acts first in one direction and then the other which causes valve element 8 to vibrate. The

vibration, of course, is permitted because the connecting means 4 includes a yielding connection such as a spring 38. Thus the power employed to produce vibration of valve stem 8 is taken from the source of fluid supply which is controlled by the valve stem 8. The unbalanced forces pro duced at the outlet of the valve together-with'the resilient mounting of the valve stem, results in the desired vibration. By incorporating in conmotion '4' sumcient massfth'e amplitude and frequency of the vibration may be caused to assume any desired or necessary value for satisfactory and reliable operation.

Connecting means 4' comprises a relatively still spring, the upper end of which is threaded onto a stud 39 which in turn is secured to the interior of a socket member 44 by means 01' a screw i. Socket member 40 is carried by a connecting link 42 which is secured to backing plates 43 disposed on either side of flexible member 2. The point where this link passes through the housing casing I is sealed by means or a sealing diaphragm M which is of such thinness and flexibility that it oflers substantially no resistance to movement of diaphragm 2 or the parts connected thereto. The upper side of the diaphragm is connected to means 45 for counterbalancing the weight oi. the diaphragm 2 and the connecting means s' and valve stem 8 so that the pressures acting 'on diaphragm 2 need not be wasted in overcoming turn is secured to the socket member by means of screws 52. Ring bi bears on the cage of the anti-friction bearing as shown in Fig. 1. The lower end of the socket member carries a propeller 53 which may be in the form or a disc formed with vanes 58 at its outer edge having the appearance of paddles. A jet of oil is utilized as a convenient form of power for turning the propeller. This jet of oil or fluid is derived from the supply of motive fluid delivered to inlet i3 01' the valve body. A pipe 5 is connected to pipe I! which is so shaped that a nozzle 85' secured thereto causes fluid in the form of a high velocity Jet to strike or impinge on the paddles oi the propeller and causes it to spin much in the same fashion as a turbine wheel is caused to turn when a Jet of fluid is directed against its buckets. I

Valve stem 8 is secured to a socket member 50 by means of set screws 56. Thus as the impeller is spun by the jet of fluid issuing from nozzles 65', valve stem ii is caused to spin. The

speed at which the valve stem 8 is spun may be varied or limited to any desired value by proper shaping of the impeller and the type-of nozzle v employed for directing the motivating Jet against the vanes thereof. By making the socket memer and the impeller of suificient weight the 7 ivibratory system comprising the spring, the

:socket, its bearing, and the impeller may be caused to vibrate at the proper frequency as the result of the action of thefluid on lands i0 and weight or the force of weight-balancing springs.

The point where connecting link 42 passes through the upper side or housing 3 is sealed by means of a sealing diaphragm 46 which is side of the diaphragm need be exposed to thepressure-which is to be regulated, in which case the other side of the diaphr may be opened to the atmosphere so that the diaphragm will move in response to changes in the pressure to be regulated.

The lower end of the spring 383 is threaded onto a threaded stud ll. The lower end of this stud carries an anti-friction bearing tit) which is secured to the lower end of the stud by means of a screw 49. This bearing is caged in a socket member 88 which is secured to the bearing by means of an annular flange or ring 5! which in H controlling the outlet ports oi the valve. It has been observed in the actual operation of the device that when valve stem 8 is in the neutral position the amplitude of vibration is maxim and that as the valve is moved either up or down and away from the neutral position the ampli tude of vibration seems to become less, although the frequency of vibration does not appear to change materially if at all. and that vibration LI" its wide-open positions.

By spinning and vibratin valve stem 8 as above described, it has been found that valve stem 8- may be moved throughout its full range of travel in response to a pressure change as low as 0.001

of an inch of water. It has also been observed in actual operation of this valve that the valve may be moved on the slightest or minutest change in pressure. Since the valve does not stick and static friction does not have to be overcome, the response of diaphragm 2 to pressure changes results in almost immediate movement of valve stem 8.

I have shown in Fig. 2 the counterbalancing mechanism which supports the weight or the diaphragm 2 and its backing plates and the connection between the diaphragm and valve stem as comprising a lever 57 which is mounted on a knife-edge 58, at a point intermediate its ends.

One end of the lever is connected to a link 89:

counterweight and the diaphragm and the mechanism suspended rrcm it and connected valve stem 8. may be obtained, to

Where minute pressure changerare to be utilized in causing full range movement of valve when the valve is in one or the other oi" cylinder ll.

' ample, in order to produce a change in loading tension on the diaphra m equivalent to a presssurcactingonthediaphragmoitheorderod 0.001 inch of water.

The operation device I will be readily understood from the application of it to the control of a power cylinder as illustrated in Fig. '1. In this illustration, the pressure drop across an orifice B4 in a conduit 8| is tobe maintained substantially constantbymeansoi adamperor valve ll connected to the piston of the power One side of the orifice is connected by apipe lltoonesideoi diaphragm 2 andthe other side oi the diaphragm is connected by pipe II to the other side of the orifice. Thus when'a gaseous iiow occurs, the pressure drop developed is imposed on the diaphragm. Assuming that pump I4 is supplying fluid under pressure to the inlet of valve 4 and that device I has been adiusted until valve It is in the proper position to eilect a how that produces the desired pressure drop, then valve stem I will be in neutral position, spinning and vibrating. While it remains in this position the fluid pressures on each side of the pistonin cylinder II will be equal and there will be a slight but continuous discharge of fluid from exhaust ports 23 and 24. It the pressure drop increases this indicates that valve I. should be adjusted towards closed position. In response to the increase in pressure drop, diaphragm 2 moves downwardly whereby the inlet II is connected to outlet 0! the valve leading to the lower end of cylinder 20 and the top,

of cylinder 2| is connected to exhaust whereby the piston in cylinder 20 moves upwardly. As it moves upwardly. the pressure drop across orifice ll decreases and when the desired pressure drop is attained movement of the piston stops because valve stem will have been returned to neutral position again. It the pressure drop decreases below the value desired valve stem 8 is moved upwardly and this causes fluid pressure to act on the top of the piston in cylinder 20, which fluid is exhausted from the lower end 0! the cylinder. This results in the damper or valve 06 being moved towards open position until the desired pressure drop is attained. As the desired value of pressure drop is approached, valve stem 8 is gradually being returned to neutral position.

It will be apparent from the above that when .slight departures from the desired pressure drop occur valve stem 8 will be moved relativelyslowly and by small amounts but that when the departure is large, valve stem I will be moved quickly andtowards a wide-open position, cansing the piston in the power cylinder to move rapidly and if necessary with a long stroke until the pressure change is restored to the desired value.

Having thus described the invention, what I claim as new and desire to secure by Letters Patent is:

l. A regulating device comprising a pressuresensitive member, a valve having a movable control element, means yieldingly connecting said movable control element to said pressure-sensitive member. and means for continuously spinning said control element to reduce static iristlonbetween said control element and its operating valve parts.

- 2. A regulating device comprising a pressuresensitive member, a valve having a movable control element, means yieldingly connecting said movable control element to said pressure-sensitive member, means for continuously spinning said control element to reduce static friction between said control element and its cooperating valve parts, and means for causing said control element to vibrate in a direction coincidental with the direction in which it is moved by said pressure-sensitive member.

3. A regulating device comprising apressuresensitive member, a valve including a ported I member and a control element disposed to control the ports oi said ported member, means rotating said control element relative to said ported member, means for vibrating said con-.

trol element, and a resilient connection between said pressure-sensitive member and said valve control element.

4. In combination a valve having a movable control element, means for actuating said mov-' able control element, a rotatable coupling connected to said control element, means yieldingly connecting said actuating means to said coupling, and means for rotating said coupling whereby said control element is rotated in said valve, the rotation of said control element eilectively reducing static friction in said valve.

5. A combination according to claim 4 characterized by the fact that the rotating means includes an impeller member and a nozzle for directing a Jet of motive fluid against said impeller causing it to rotate said coupling and the movable control element of said valve.

8. A combination according to claim 4 characterized by the fact that the rotating means includes an impeller member and a nozale for directing a jet of motive fluid against said im peller causing it to rotate said coupling and th movable control element of said valve, and me for vibrating said movable control element the direction in which it is moved by said actu-- ating means.

7. A static friction-free pilot valve mechanism comprising a valve assembly having ported member and a valve element for controlling the ports of said ported member, a resilient support ior said valve element, an actuator for moving the valve element, and means for effecting relative rotation between the ported member and the valve element.

8. A valve mechanism according to claim '7 characterized by the fact that means are provided for rotating one of the, valve assembly elements to effect relative rotation between the ported element and the valve element.

9. A valve mechanism according to claim '1 characterized by the fact that the valve element is provided with lead so that when there is flow throughilzhe valve and the valve element is in 1 or near its neutral position the valve element vibrates in the direction in which it is disposed to be moved by the actuator.

ROBERT R. DONALDSON. 

